Planetary gear ball valve

ABSTRACT

A stemless ball valve comprising a first flange, second flange, ball, inner magnetic cartridge, outer magnetic cartridge, and planetary gear assembly. The inner magnetic cartridge is situated inside of the outer magnetic cartridge, and the inner and outer magnetic cartridges actuate the valve. The planetary gear assembly is situated between the inner magnetic cartridge and the ball. The planetary gear assembly comprises one or more planetary gear phases, each planetary gear phase comprising a step-down gear. Each planetary gear phase comprises one or more planetary gears that engage with the inner teeth of the outer ring of the planetary gear assembly and with a step-down gear. The invention further comprises a pressure equalization system comprising inner and outer equalization tubes, a piston situated between the inner and outer equalization tubes, and either a piston spring or spring washer stack that biases the piston in the direction of the clean oil.

CROSS-REFERENCE TO RELATED APPLICATION

This application is a continuation-in-part of U.S. patent applicationSer. No. 13/010,827 filed on Jan. 21, 2011.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates generally to the field of valves, and moreparticularly, to a stemless ball valve that utilizes a planetary gearassembly to increase torque from the valve handle to the ball.

2. Description of the Related Art

The present invention represents an evolution in ball valve technologybeginning with the stemless ball valve disclosed in U.S. patentapplication Ser. No. 12/331,387, wherein the ball is actuated by anouter magnetic cartridge in magnetic contact with an inner magneticcartridge that rotates a guide sleeve. The guide sleeve has guidechannels into which travel pins on the ball are inserted. The guidechannels are shaped and the travel pins are situated so that as theguide sleeve rotates, the travel pins travel inside the guide channels,thereby rotating the ball.

The next related evolution in stemless ball valve technology isrepresented by the invention disclosed in U.S. patent application Ser.No. 12/890,645. In this invention, the guide sleeve that was situatedinside of the inner magnetic cartridge is moved so that it is adjacentto and outside of the inner magnetic cartridge but secured to the innermagnetic cartridge so that when the inner magnetic cartridge rotates,the cartridge guide holder also rotates. The guide sleeve is situatedinside of the cartridge guide holder and comprises guide channels intowhich the travel pins on the ball are inserted. Thus, the ball isrotated in the same manner as in the previous invention, except that alarger ball can be used because the cartridge guide holder and guidesleeve are no longer inside of the inner magnetic cartridge, butadjacent to it. The larger ball allows for a valve with greater flowcapacity.

Although the two inventions described above solve many of the problemsassociated with stemmed ball valves, one major drawback of these valvesis that they have not been able to match the torque requirements ofstemmed valves. In addition, magnetically-actuated valves tend toexperience hysteresis, which is a lag that occurs between the outer andinner magnetic cartridges and that becomes more pronounced as the torquerequired to power a given valve element approaches the maximum torqueavailable from the magnetic drive. When hysteresis is pronounced,slippage may occur between the inner and outer magnetic cartridges,causing the valve to malfunction.

Stemless ball valves are desirable over stemmed valves because there isno penetration from outside of the valve into the valve body. This lackof penetration from the outside reduces emissions and prevents leakage.Until now, the torque of stemless ball valve designs was limited by thetorque that could be provided by the magnetic interlock between theinner and outer magnetic cartridges. What was needed was a stemless ballvalve that could provide the same torque as a stemmed valve while stillproviding a leak-free environment.

As described more fully below, the present invention solves this problemby interposing a planetary gear assembly between the inner magneticcartridge and the ball. This planetary gear assembly greatly increasesthe torque from the handle outside of the valve (the handle beingcoupled to the outer magnetic cartridge) to the ball itself, therebyallowing the valve to operate effectively in applications that requirehigher torque, while still providing the advantages of a stemless ballvalve.

BRIEF SUMMARY OF THE INVENTION

The present invention is a stemless ball valve comprising: a firstflange; a second flange: a ball; an inner magnetic cartridge; an outermagnetic cartridge; and a planetary gear assembly; wherein the innermagnetic cartridge is situated inside of the outer magnetic cartridge,and wherein the inner and outer magnetic cartridges actuate the valve;and wherein the planetary gear assembly is situated between the innermagnetic cartridge and the ball. In a preferred embodiment, theplanetary gear assembly comprises one or more planetary gear phases, andeach planetary gear phase comprises a step-down gear. Each step-downgear has a width, and the width of each step-down gear preferablyincreases from the planetary gear phase closest to the inner magneticcartridge to the planetary gear phase closest to the ball.

In a preferred embodiment, each planetary gear phase comprises one ormore planetary gears, the planetary gear assembly comprises an outerring with inner teeth, and each planetary gear engages with the innerteeth of the outer ring and with a step-down gear. The inner magneticcartridge is preferably attached to the planetary gear phase that isclosest to the inner magnetic cartridge. The invention preferablyfurther comprises a bull gear on at least one side of the ball, and thebull gear is preferably attached to the planetary gear phase that isclosest to the ball.

In a preferred embodiment, the present invention further comprises aball gear that is attached to the ball, the bull gear and the ball geareach comprises a plurality of teeth, and the teeth on the bull gearengage with the teeth on the ball gear so that when the bull gearrotates, it causes the ball to rotate. The invention preferably furthercomprising a trunnion axle, the ball gear comprises a center, and thetrunnion axle preferably passes through the center of the ball gear.

In a preferred embodiment, the present invention further comprises atrunnion bearing, the ball gear comprises a base portion, the trunnionbearing is situated inside of the base portion of the ball gear, and thetrunnion axle rotates inside of the trunnion bearing. The trunnion axleis preferably secured to the second flange.

In a preferred embodiment, the present invention further comprises aflow tube, the valve has a flow path, and the flow tube is situatedbetween the inner magnetic cartridge and the flow path. The inventionpreferably further comprises two ball gear seal rings that form a collararound the ball. The invention preferably further comprises a springseal that is situated between the flow tube and one of the two ball gearseal rings.

In a preferred embodiment, the present invention further comprises abull gear on at least one side of the ball, the bull gear is attached tothe planetary gear phase that is closest to the ball, the inventionfurther comprises a ball gear that is attached to the ball, the bullgear and the ball gear each comprises a plurality of teeth, the teeth onthe bull gear engage with the teeth on the ball gear so that when thebull gear rotates, it causes the ball to rotate, and the planetary gearassembly, bull gear and ball gear are all located outside of the flowpath. The invention preferably further comprises a ball seat on eitherside of the ball. The invention preferably further comprises a ball stopon the ball that interacts with the second flange to prevent the ballfrom rotating more than ninety degrees.

In an alternate embodiment, the invention further comprises a pressureequalization system comprising an inner pressure equalization tube andan outer pressure equalization tube, wherein the inner equalization tubeis situated inside of the outer equalization tube, and a piston andpiston spring are situated between the inner and outer equalizationtubes. In a preferred embodiment, the inner and outer equalization tubeseach has a threaded end, and the piston spring biases the piston towardthe threaded end of the inner and outer equalization tubes.

In one embodiment, the inner and outer equalization tubes are situatedbetween the ball and the first flange. In another embodiment, the innerand outer equalization tubes are situated between the ball and thesecond flange. Preferably, the piston comprises at least one recess, andan O-ring is situated in the recess to provide a seal between the pistonand the outer equalization tube.

In an alternate embodiment, the invention comprises a pressureequalization system comprising an inner pressure equalization tube andan outer pressure equalization tube. wherein the inner equalization tubeis situated inside of the outer equalization tube, and a piston andspring washer stack are situated between the inner and outerequalization tubes. In a preferred embodiment, the inner and outerequalization tubes each has a threaded end, and the spring washer stackbiases the piston toward the threaded end of the inner and outerequalization tubes.

In one embodiment, the inner and outer equalization tubes are situatedbetween the ball and the first flange. In another embodiment, the innerand outer equalization tubes are situated between the ball and thesecond flange. Preferably, the piston comprises at least one recess, andan O-ring is situated in the recess to provide a seal between the pistonand the outer equalization tube.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of the valve fully assembled.

FIG. 2 is a side view of the valve fully assembled.

FIG. 3 is an exploded view of the valve.

FIG. 4 is a cutaway view of the valve showing the various assembliesthat comprise the valve.

FIG. 5 is an exploded view of the magnetic cartridge assembly.

FIG. 6 is an exploded view of the flow tube assembly.

FIG. 7 is an exploded view of the planetary gear assembly.

FIG. 8 is a first partial exploded view of the planetary gear assembly.

FIG. 9 is a second partial exploded view of the planetary gear assembly.

FIG. 10 is a section view of the planetary gear assembly.

FIG. 11 is a cutaway view of the planetary gear assembly.

FIG. 12 is an exploded view of the ball assembly.

FIG. 12A is a perspective view of the single bull gear embodiment.

FIG. 13 is an exploded view of the flange assembly.

FIG. 14 is a perspective section view of the magnetic cartridge assemblyshowing the inner and outer magnetic cartridges.

FIG. 15 is a section view of the magnetic cartridge assembly showing theorientation of the magnets comprising the inner and outer magneticcartridges.

FIG. 16 is a partial exploded view of the inner magnetic cartridge andthe planetary gear assembly.

FIG. 17 is a perspective view of the inner magnetic cartridge attachedto the planetary gear assembly.

FIG. 18 is an exploded view of the second flange and planetary gearassembly.

FIG. 19 is a cropped perspective view of the second flange and planetarygear assembly.

FIG. 20 is an exploded view of the bull gear and planetary gearassembly.

FIG. 21 is a perspective view of the bull gear attached to the planetarygear assembly.

FIG. 22 is a perspective view of the bull gear and ball gear with thevalve in an open position.

FIG. 22A is cropped perspective view illustrating operation of the ballstop on the ball gear.

FIG. 23 is a perspective view of the bull gear and ball gear with thevalve in a partially open position.

FIG. 24 is a perspective view of the bull gear and ball gear with thevalve in a closed position.

FIG. 25 is an exploded section view of those parts of the valve thatseal off the gear compartment.

FIG. 26 is a section view of the valve illustrating the flow path andthe position of the ball seat relative to the ball.

FIG. 27 is a perspective cutaway view of the same components shown inFIGS. 25 and 26.

FIG. 28 is a perspective view of the ball, ball gears and ball seat withthe valve in an open position.

FIG. 29 is a perspective view of the ball, ball gears and ball seat withthe valve in a partially open position.

FIG. 30 is a perspective view of the ball, ball gears and ball seat withthe valve in a closed position.

FIG. 31 is a perspective cutaway view of the ball assembly positioned inthe second flange.

FIG. 32 is a first perspective view of the ball assembly illustratingthe interaction between the bull and ball gears.

FIG. 33 is a second perspective view of the ball assembly illustratingthe interaction between the bull and ball gears.

FIG. 34 is a perspective view of the pressure equalization system of thepresent invention.

FIG. 35 is a section view of the pressure equalization system of thepresent invention.

FIG. 36 is an exploded view of the pressure equalization system of thepresent invention.

FIG. 37 is a section view of the present invention shown with thepressure equalization system.

FIG. 38 is a cutaway view of the pressure equalization system of thepresent invention.

FIG. 39 is a cutaway view of the pressure equalization system shown witha spring washer stack in lieu of a piston spring.

REFERENCE NUMBERS

1 First flange

2 Second flange

3 Handle (wheel actuator)

4 Outer magnetic cartridge

5 Bolt

6 Screw

7 Magnetic cartridge assembly

8 Flow tube assembly

9 Planetary gear assembly

10 Ball assembly

11 Flange assembly

12 Tube

13 Inner magnetic cartridge

14 Bull gear

15 Ball gear

15 a Base (of ball gear)

16 Ball

17 Ball seat

18 Trunnion (trunnion axle)

18 a Channel (in trunnion)

19 O-ring

20 Spring seal

21 Rubber gasket

22 Outer ring

23 Inner teeth (of outer ring)

24 First disc

25 First step-down gear

26 Planetary gear (of first planetary gear phase)

27 First planetary gear phase

28 Second step-down gear

29 Planetary gear (of second planetary gear phase)

30 Second planetary gear phase

31 Third step-down gear

32 Planetary gear (of third planetary gear phase)

33 Third planetary gear phase

34 Interface disc (of first planetary gear phase)

35 Circular bracket (of first planetary gear phase)

36 Pin

37 Interface disc (of second planetary gear phase)

38 Circular bracket (of second planetary gear phase)

39 Circular bracket (of third planetary gear phase)

40 Interface disc (of third planetary gear phase)

41 Ball gear seal ring

42 Trunnion bearing

43 Key

44 Slot

45 Male part (of bull gear)

46 Female part (of bull gear)

47 Outer equalization tube

47 a Aperture (in outer equalization tube)

48 Inner equalization tube

48 a Recess (in inner equalization tube)

49 Piston

50 Piston spring

51 Spring washer stack

52 Grease fitting

53 Grease pathway

100 Valve

DETAILED DESCRIPTION OF INVENTION

The present invention is a stemless ball valve that utilizes a planetarygear assembly to increase torque from the handle (wheel actuator) of thevalve to the ball. The planetary gear assembly is situated between theinner and outer magnetic cartridges, which are in magnetic contact withone another, and the ball itself. The ball comprises two ball gears thatare in contact with a bull gear that surrounds the ball. As the bullgear rotates, it causes the ball gears to rotate, thereby rotating theball and opening and closing the valve. The bull gear in turn is coupledto the last of the planetary gear phases. In a preferred embodiment, thevalve trunnions (or trunnion axles) pass through the center of each ballgear, and the ball rotates on the trunnions. The entire gear system—theplanetary gear assembly, bull gear and ball gears—is located outside ofthe flow path so as to prevent debris from coming into contact with thegears.

The present invention is not limited to any particular number of phasesin the planetary gear assembly, but the preferred embodiment comprisesthree phases. The first planetary gear phase is coupled to the innermagnetic cartridge; the second planetary gear phase is coupled to thethird planetary gear phase; and the third planetary gear phase iscoupled to the hull gear. Due to the unique structural configurationdescribed below and illustrated in the accompanying figures, the torqueof the valve is increased with each phase of the planetary gearassembly. The planetary gear assembly also decreases the rate ofrotation with each phase so that the bull gear rotates at a greatlyreduced rate relative to the rotation of the inner magnetic cartridge.

In this manner, the torque applied to the wheel actuator is amplified bythe time it reaches the bull gear on the other end of the planetary gearassembly. In the preferred embodiment shown in the figures and describedbelow, the torque between the inner magnetic cartridge and the bull gear(which drives the ball gears on the ball) is multiplied by a factor of13.2—a significant advantage over previous stemless ball valve designs.Another advantage of the present invention is that the magnetic drivesystem (i.e., the inner and outer magnetic cartridges) is able tooperate at a fraction of its total power capability and yet still havesufficient torque available to actuate the valve, thereby avoiding thehysteresis issue described above.

The planetary gear assembly of the present invention reduces the overalltorque requirements of the magnetic drive system, but it also requiresmuch more motion at the upper (actuating) end. In the preferredembodiment, the planetary gear assembly increases torque to the valve bya factor of roughly 13:1, but it also requires 13 times more rotationfrom the inner magnetic cartridge in order to turn the valve. By way ofexample, a quarter-turn ball valve (90 degrees of rotation) requires1170 (13 times 90) degrees of motion from the inner magnetic cartridge,or 3¼ A complete rotations, in order to move the valve ¼ turn.

This requirement of increased motion at the upper end of the valve isactually an advantage when the outer cartridge of the magnetic drivesystem is powered by an electric or pneumatic motor because the accuracyof the motor is enhanced by a factor of 13. For example, if an electricmotor has a ten-degree margin of error in position, that error isreduced 13 times by the planetary gear assembly, and the resulting errorin the position of the valve is less than one degree.

FIG. 1 is a perspective view of the valve fully assembled. This figureshows a first flange 1, a second flange 2, a handle 3 (also referred toas the “wheel actuator”), and an outer magnetic cartridge 4. Bolts 5(for ease of reference, the bolts and corresponding nuts are bothlabeled as reference number 5) are used to secure the valve to piping(not shown). Bolts 5 are also used to secure the first and secondflanges to each other and to hold the trunnions 18 (also referred to asthe “trunnion axles”), which pass through the center of the ball gears15 on the ball 16 (see FIG. 4), in place. In a preferred embodiment, thebolts 5 do not thread into the trunnions 18 but rather abut up againstthem to prevent the trunnions from pushing outward due to the force ofthe flow in the valve. As shown more clearly in. FIGS. 4 and 12, thetrunnions rotate inside of a trunnion bearing 42 that is press fit intothe base 15 a of the ball gear 15.

As shown more clearly in FIG. 5, the outer magnetic cartridge 4 ispreferably comprised of two semi-circular halves that are joinedtogether with screws 6. The wheel actuator 3 is also preferablycomprised of two semi-circular parts that are joined together withscrews 6. FIG. 2 is a side view of the valve fully assembled.

FIG. 3 is an exploded view of the valve 100. This figure shows thevarious assemblies comprising the valve, each of which is shown infurther details in subsequent figures. The magnetic cartridge assembly 7provides the magnetic actuation for the valve. The flow tube assembly 8provides a flow path for the valve and a magnetic barrier between theinner and outer magnetic cartridges. The planetary gear assembly 9provides the increase in torque from the inner magnetic cartridge to thebull gear (included in the ball assembly). The ball assembly 10 includesthe bull gear, ball gears and ball. The flange assembly 11 secures thetrunnion axles to the second flange. Each of these sub-assemblies isdescribed below in greater detail.

FIG. 4 is a cutaway view of the valve showing the various assembliesthat comprise the valve. This figure shows the tube 12 of the flow tubeassembly 8, the inner magnetic cartridge 13 of the magnetic cartridgeassembly 7, the planetary gear assembly 9, the bull gear 14 and one oftwo ball gears 15 (see also FIG. 12) on the ball 16. A ball seat 17 liesbetween the ball 16 and the second flange 2 (see FIG. 13 for greaterclarity). As noted above, the trunnion axles 18 pass through the centerof each ball gear 16 and are secured to the second flange 2 with bolts5.

FIG. 5 is an exploded view of the magnetic cartridge assembly. Thisfigure shows the first flange 1, the wheel actuator 3, the outermagnetic cartridge 4, and the inner magnetic cartridge 13. It also showsthe O-rings 19 that lie on either side of the outer magnetic cartridge 4and between the first and second flanges 1, 2. Note that a portion ofthe first flange 1 is situated between the inner and outer magneticcartridges 13, 4 so that the two magnetic cartridges do not physicallycome into contact with one another. The wheel actuator 3 is preferablybolted onto the outer magnetic cartridge 4 so that as the wheel actuator3 rotates, the outer magnetic cartridge 4 rotates as well. The inner andouter magnetic cartridges 13, 4 are aligned so that they are inmagnetic, but not physical, contact with one another (see also FIGS. 14and 15); therefore, rotation of the outer magnetic cartridge 4 causesthe inner magnetic cartridge 13 to rotate in the same direction.

FIG. 6 is an exploded view of the flow tube assembly. The function ofthe flow tube 12 is to act as a physical barrier between the magneticcartridge assembly 7 and the flow path, provide a rigid sealing surfacefor the ball seat 17, and protect the flow path from magnetic fieldsthat could disrupt the flow. The reason it is important to create abarrier between the magnetic cartridge assembly 7 and the flow path isto avoid creating a magnetic field in the flow path that might causedebris to build up around the insides of the flow path (tube), therebydecreasing the rate of flow and rendering the valve less effective. Thethickness of the flow tube 12 will depend on the strength and size ofmagnets used in the inner and outer magnetic cartridges and whatpercentage of the magnetic field needs to be blocked out from the flowpath.

FIG. 6 also shows the O-ring 19 that lies between the flow tube 12 and,the first flange 1. In a preferred embodiment, a rubber gasket 21 liesbetween the flow tube 12 and the ball seat 17, and a spring seal 20 liesbetween the flow tube 12 and ball gear seal ring 41 (not shown). Thespring seal 20 acts as a seal between the flow tube 12 and the ball gearseal ring 41. The rubber gasket 21 acts as a spring that holds the ballseat 17 against the ball 16, and it also acts as a seal between the flowtube 12 and the ball seat 17. As shown in this figure and FIGS. 13 and26, the ball seat 17 comprises two halves that together form a collararound the ball 16.

FIG. 7 is an exploded view of the planetary gear assembly. As shown inthis figure, the planetary gear assembly 9 comprises an outer ring 22with inner teeth 23 that extend around the inner perimeter of the outerring 22. In this embodiment, three phases of planetary gears are shown,but the present invention is not limited to any particular number ofplanetary gear phases. The planetary gear assembly 9 comprises a firstdisc 24 that is attached to the inner magnetic cartridge 13 (not shown)and that rotates with the inner magnetic cartridge 13. The first disc 24comprises a first step-down gear 25 that turns the planetary gears 26 onthe first planetary gear phase 27. The first planetary gear phase 27comprises a second step-down gear 28 that turns the planetary gears 29on the second planetary gear phase 30. The second planetary gear phase30 comprises a third step-down gear 31 that turns the planetary gears 32on the third planetary gear phase 33. The third planetary gear phase 33has no step-down gear because it is attached to the bull gear 14 (notshown).

Each planetary gear phase preferably comprises three planetary gears,but the present invention is not limited to any particular number ofplanetary gears per planetary gear phase. Note that the planetary gearsof each planetary gear phase engage with the teeth 23 on the inside ofthe outer ring 22 as well as with the teeth on the step-down gear of theprevious planetary gear phase. Note also that the step-down gears 25,28, 31 are increasingly wider as compared to the previous step-downgear; the reason for the increase in width of the step-down gears isbecause the torque is increasing from one planetary gear phase to thenext.

FIG. 8 is a first partial exploded view of the planetary gear assembly.This figure shows the outer ring 22, first disc 24 and first planetarygear phase 27. The first planetary gear phase 27 comprises an interfacedisc 34, three planetary gears 26, and a circular bracket 35 comprisingthe first step-down gear 28. Pins 36 or other fastening mechanisms areused to secure the first disc 24 to the inner magnetic cartridge 13 (notshown), and screws 6 are used to secure the circular bracket 35 to theinterface disc 34.

FIG. 9 is a second partial exploded view of the planetary gear assembly.As shown in this figure, the second planetary gear phase 30 comprises aninterface disc 37, three planetary gears 29, and a circular bracket 38comprising the second step-down gear 28. The third planetary gear phase33 comprises a circular bracket 39 that houses the planetary gears 32and an interface disc 40. The circular bracket 39 of the third planetarygear phase (or whichever planetary gear phase is the last one before thebull gear) does not comprise a step-down gear. Screws 6 or otherfastening mechanisms are used to secure the circular bracket 38 to theinterface disc 37 of the second planetary gear phase 30 and the circularbracket 39 to the interface disc 40 of the third planetary gear phase33.

FIG. 10 is a section view of the planetary gear assembly. This section,view is taken through the middle of the circular bracket 38 of thesecond planetary gear phase 30. In this figure, the step-down gear 31 onthe circular bracket 38 of the second planetary gear phase 30 is notshown because the section has been taken behind it. The planetary gears29 of the second planetary gear phase 30 are engaged with the innerteeth 23 on the outer ring 22 and also with the step-down gear 28 of thefirst planetary gear phase 27.

FIG. 11 is a cutaway view of the planetary gear assembly. This figureshows the first disc 24 and first, second and third planetary gearphases 27, 30, 33 in their assembled state.

FIG. 12 is an exploded view of the ball assembly. The ball assembly 10comprises a bull gear 14, which, as shown in this figure, is comprisedof two halves that surround the ball 16. The ball assembly 10 alsocomprises a ball gear seal ring 41 on either side of the ball 16 thatprovides a seal around the base 15 a of the ball gear 15. Pins 36 attachone half of the bull gear 14 to the interface disc 40 (see FIG. 9) ofthe third planetary gear phase 33 so that the bull gear 14 turns at thesame rate as the third planetary gear phase 33. In a preferredembodiment, the outside diameter of the bull gear 14 is the same as theoutside diameter of the interface disc 40 of the third planetary gearphase 33 (and as the circular bracket 39 of the third planetary gearphase 33), but the present invention does not require that the outsidediameter of the bull gear 14 be the same as the outside diameter of theinterface disc 40 or the circular bracket 39.

The ball gears 15 are situated on either side of the ball 16 and arepreferably press fit into the ball 16. Note that the teeth on the ballgear do not extend around the entire perimeter of the ball gear, nor dothe teeth on the bull gear 14. The reason the teeth do not extend aroundthe entire perimeter of the ball gears or the bull gear is because theyonly need to turn the ball 16 ninety degrees)(90° to open and close thevalve. In between the ball gears 15 and the ball 16 are O-rings 19.Although the ball gear 15 is shown in the figures as a bevel gear (Le.,with a flat base and a beveled top), the present invention is notlimited to any particular configuration of the ball gear as long as itcomprises teeth that engage with the bull gear.

A trunnion axle 18 extends through a trunnion bearing 42 and through thecenter of each ball gear 15. The trunnion bearing 42 is situated insideof the base 15 a of the ball gear 15 and surrounds the end of thetrunnion axle 18 that is inserted into the ball gear 15. As explainedabove, the trunnion 18 rotates within the trunnion bearing 42. An O-ring19 is preferably inserted around each of the trunnion axles at a channel18 a in the perimeter of the trunnion axle 18. The O-ring 19 secures thetrunnion 18 inside of the second flange 2 and prevents it from rotating.

Although FIG. 12 shows two a single bull gear comprised of two halves,the present invention could operate with only one half of the bull gear14, as shown in FIG. 12A, and a single ball gear 15. In this embodiment,there is a bull gear 14 (comprised of one half of the bull gear 14 shownin FIG. 12) and a single ball gear 15, and the single bull gear 14causes the ball gear 15 to rotate (thereby rotating the ball 16), asdescribed above. The two-part bull gear and two ball gears arepreferred, however, for strength and stability of the valve. As used inthe claims, the term “bull gear” refers either to the bull gearembodiment comprised of two halves and shown in FIG. 12 or to the bullgear embodiment comprised of a single half and shown in FIG. 12A.

FIG. 13 is an exploded view of the flange assembly. This figure showsthe second flange 2 and the bolts 5 that secure the trunnion axles 18(not shown) in the second flange. This figure also shows the bolts 5that are used to secure the second flange 2 to the first flange 1. (Thebolts that secure the second flange 2 to the piping are not shown.) Alsoshown are the other half of the ball seat 17 and the rubber gasket 21that lies between the ball seat 17 and the second flange 2. The springseal 20 is situated between the second flange 2 and the ball gear sealring 41.

An important design aspect of the present invention is that much of theforce being applied to the ball 16 is able to be absorbed by thetrunnion axles 18. In previous stemless ball valve designs, the sealstook much of the force, which caused them to wear out more quickly. Byusing heavy duty trunnion axles, the pressure—which can exceed severaltons—is taken off of the downstream seal and ball seat and applied tothe heavy trunnion axles.

FIG. 14 is a perspective section view of the magnetic cartridge assemblyshowing the inner and outer magnetic cartridges. As shown in thisfigure, the inner magnetic cartridge 13 lies inside of the outermagnetic cartridge 4 with a portion of the first flange 1 in betweenthem.

FIG. 15 is a section view of the magnetic cartridge assembly showing theorientation of the magnets comprising the inner and outer magneticcartridges. This figure is illustrative of a preferred orientation ofthe inner 13 a and outer 4 a magnets, but the present invention is notlimited to any particular configuration of the magnets within the inner13 and outer magnetic cartridges 4. In this figure, the flow path isdesignated with an “X.”

FIG. 16 is a partial exploded view of the inner magnetic cartridge andthe planetary gear assembly, and FIG. 17 is a perspective view of theinner magnetic cartridge attached to the planetary gear assembly. Theplanetary gear assembly 9, and more particularly, the first disc 24 (notshown), is attached to the inner magnetic cartridge 13 with pins 36. Anymethod of attaching the planetary gear assembly 9 to the inner magneticcartridge 13 may be used.

FIG. 18 is an exploded view of the second flange and planetary gearassembly. As shown in this figure, the planetary gear assembly 9 slidesinto the second flange 2. FIG. 19 is a cropped perspective view of thesecond flange and planetary gear assembly. As shown in this figure, theplanetary gear assembly 9 is aligned within the second flange 2 byfitting the keys 43 that extend from the inner wall of the second flangeinto the slots 44 on the outer ring 22 of the planetary gear assembly 9.

FIG. 20 is an exploded view of the bull gear and planetary gearassembly, and FIG. 21 is a perspective view of the bull gear attached tothe planetary gear assembly. The bull gear 14 is attached to theplanetary gear assembly 9, and more particularly, to the interface disc40 of the third planetary gear phase 33, with pins 36. Any method ofattaching the bull gear 14 to the planetary gear assembly 9 may be used.Note that only one half of the bull gear 14 is shown in FIGS. 20 and 21;the two halves of the bull gear 14 are affixed to one another by fittinga male part 45 into a female part 46 on each half of the bull gear 14.

FIG. 22 is a perspective view of the bull gear and ball gear with thevalve in an open position, FIG. 23 is a perspective view of the bullgear and ball gear with the valve in a partially open position, and FIG.24 is a perspective view of the bull gear and ball gear with the valvein a closed position. These three figures illustrate the position of theball relative to the bevel 15 and bull 14 gears.

FIG. 22A shows the ball stop 15 b protruding from the top of the ballgear 15. The second flange 2 preferably comprises a channel 2 a in whichthe ball stop 15 b resides. The length of the ball stop 15 b and thelength of the channel 2 a are such that the ball stop 15 b prevents theball from rotating more than ninety degrees (90°).

FIG. 25 is an exploded section view of those parts of the valve thatseal off the gear compartment. FIG. 26 is a section view of the valveillustrating the flow path and the position of the ball seat relative tothe ball.

FIG. 27 is a perspective cutaway view of the same components shown inFIG. 25. This figure shows the flow tube 12 in relation to the ball gearseal rings 41 that surround the ball 16. This figure also shows thespring seal 20 that is situated between the ball gear seal ring 41 andthe second flange 2. The spring seal 20 that is shown in this figure isthe same one that is shown in FIG. 13. The ball seat 17 keeps any solidparticles form interfering with the gears when the valve is in a fullyopen position, and the flow tube 12 and ball gear seal rings 41 keep anysolid particles from interfering with the gears when the valve is in anyposition other than fully open. Note that the two ball gear seal rings41 on either side of the ball form a collar around the ball, aspreviously stated.

FIG. 28 is a perspective view of the ball, ball gears and ball seat withthe valve in an open position, FIG. 29 is a perspective view of theball, ball gears and ball seat with the valve in a partially openposition, and FIG. 30 is a perspective view of the ball, ball gears andball seat with the valve in a closed position. These three figures showin greater detail the orientation of the ball 16 and ball gears 15 inrelation to the ball seat 17.

FIG. 31 is a perspective cutaway view of the ball assembly positioned inthe left flange. This figure differs from FIG. 27 in that it shows thetrunnions 18 that extend into the second flange 2 and the center of theball gears 15. It also shows the bull gear 14 and ball gear seal ring41. The spring seal 20, rubber gasket 21 and ball seat 17 are alsoshown.

FIG. 32 is a first (top) perspective view of the ball assemblyillustrating the interaction between the bull and ball gears, and FIG.33 is a second (bottom) perspective view of the ball assemblyillustrating the interaction between the bull and ball gears. These twofigures together illustrate the direction of movement of the bull gear14 in relation to the ball gears 15, as indicated by the arrows. Thetrunnions do not rotate; instead, the ball gears 15 (which are fixedlyattached to the ball 16) rotate about the trunnions 18 via the trunnionbearing 42. The trunnion bearing 42 preferably comprises a smooth,slipper outer surface that contacts the trunnion 18.

FIG. 34 is a perspective view of the pressure equalization system of thepresent invention. In this embodiment, the tube 12 shown in FIG. 6 isreplaced with an Outer equalization tube 47 and an inner equalizationtube 48. (Part numbers 17, 20 and 21 from FIG. 6 are still used withthis embodiment.) The inner equalization tube 48 lies inside of theouter equalization tube 47, as shown. The outer equalization tube 47preferably comprises a plurality of apertures 47 a, the purpose of whichis explained below.

FIG. 35 is a section view of the pressure equalization system of thepresent invention. As shown in this figure, the inner equalization tube47 is threaded into the outer equalization tube 48 at one end of bothtubes (see “Y” on FIG. 35). There is a gap between the inner and outerequalization tubes, and in this gap are situated a piston 49 and pistonspring 50. Note that the apertures 47 a in the outer equalization tubeare situated between the piston 49 and the threaded end of the outerequalization tube. This ensures that any grease that is injected intothe valve through the grease fitting 52 (see FIG. 37) will remain on theclean oil side of the piston; that is, clean oil is injected into thevalve via the grease fitting 52, and dirty oil travels through the ball16 via the flow path (see “Z” on FIG. 37). In this manner, the piston 49prevents dirty oil from coming into contact with the planetary gearassembly.

FIG. 36 is an exploded view of the pressure equalization system of thepresent invention. As shown in this figure, the piston 49 is preferablyshaped like a ring with a central aperture of roughly the same diameteras the outside diameter of the non-threaded portion of the innerequalization tube 48. The piston 49 also preferably comprises recesses(not shown) into which O-rings 19 are inserted. These O-rings 19 createa dynamic seal between the piston 49 and the inside surface of the outerequalization tube 47. Note that the piston is not fixedly attached toany other components of the valve; instead, the piston floats on theinner equalization tube 48, as described more fully below.

As fluid pressure builds on the clean oil (non-spring) side of thepiston 49, the piston will move toward the ball 16 (see FIG. 37),thereby compressing the piston spring 50. As the piston compresses thespring 50, the spring biases the piston toward the clean oil side of thevalve (i.e., toward the threaded end of the inner equalization tube 48).When the force of the piston spring 50 is greater than the force of thefluid on the non-spring (or clean oil) side of the piston 49, then thespring will push the piston 49 back toward the clean oil side of thevalve and away from the ball 16. In this manner, the piston 49 isallowed to float on the inner equalization tube, acting as a pressureequalizer between the fluid on the clean oil side of the piston and thefluid on the dirty oil (ball) side of the piston. Note that there is noway for the dirty oil to come into contact with the planetary gearassembly unless dirty oil leaks past the piston. This is unlikely tohappen due to the presence of the spring, which is always exertingpressure toward the clean oil side of the piston, thereby ensuring thatthe fluid pressure will always be greater on that side of the piston. Ifany fluid leaks past the piston, it will likely be clean oil leakinginto dirty oil and not vice versa.

FIG. 37 is a section view of the present invention shown with thepressure equalization system. As shown in this figure and in FIG. 35,the inner equalization tube 48 preferably comprises two recesses on thethreaded end of the tube into which O-rings 19 are inserted to create aseal between the inner equalization tube 48 and the first flange 1. Thepressure equalization system creates a seal between the flange 1 and theball seat 17 on the side of the ball 16 that is closest to the pressureequalization system. Although the pressure equalization system is shownin this figure as being situated between the first flange 1 and the ball16, it could also be situated between the second flange 2 and the ball16. Where the pressure equalization system is situated relative to theball is dependent on the direction of flow; the pressure equalizationsystem is preferably situated on the upstream side of the ball.

As stated above, clean oil is injected into the valve via a greasefitting 52. This grease fitting 52 allows grease to flow among thevarious parts of the valve for lubrication purposes. The apertures 47 ain the outer equalization tube 47 allow this grease (also referred toabove as “clean oil”) to flow into the gap between the outer and innerequalization tubes 47, 48 on the clean oil side of the piston 49. Inother words, these apertures 47 a are preferably located between thepiston 49 and the threaded ends of the outer and inner equalizationtubes, as shown in FIG. 37.

FIG. 38 is a cutaway view of the pressure equalization system of thepresent invention. This figure shows all of the parts previouslydescribed in connection with FIGS. 34-37. The clean oil and dirty oilsides of the pressure equalization system are also indicated on thisfigure.

FIG. 39 is a cutaway view of the pressure equalization system shown witha spring washer stack in lieu of a piston spring. In an alternateembodiment, the piston spring 50 is replaced with a spring washer stack51. The spring washer stack 51 functions in the same manner as thepiston spring 50.

Although the preferred embodiment of the present invention has beenshown and described, it will be apparent to those skilled in. the artthat many changes and modifications may be made without departing fromthe invention in its broader aspects. The appended claims are thereforeintended to cover all such changes and modifications as fall within thetrue spirit and scope of the invention.

1. A stemless ball valve comprising: (a) a first flange; (b) a secondflange;) (c) a ball; (d) an inner magnetic cartridge; (e) an outermagnetic cartridge; (f) a planetary gear assembly; and (g) a pressureequalization system comprising an inner pressure equalization tube andan outer pressure equalization tube; wherein the inner magneticcartridge is situated inside of the outer magnetic cartridge, andwherein the inner and outer magnetic cartridges actuate the valve;wherein the planetary gear assembly is situated between the innermagnetic cartridge and the ball; and wherein the inner equalization tubeis situated inside of the outer equalization tube, and a piston andpiston spring are situated between the inner and outer equalizationtubes.
 2. The stemless ball valve of claim 1, wherein the inner andouter equalization tubes each has a threaded end, and wherein the pistonspring biases the piston toward, the threaded end of the inner and outerequalization tubes.
 3. The stemless ball valve of claim 1, wherein theinner and outer equalization tubes are situated between the ball and thefirst flange.
 4. The stemless ball valve of claim 1, wherein the innerand outer equalization tubes are situated between the ball and thesecond flange.
 5. The stemless ball valve of claim 1, wherein the pistoncomprises at least one recess_(;) and wherein an O-ring is situated inthe recess to provide a seal between the piston and the outerequalization tube.
 6. A stemless ball valve comprising: (a) a firstflange; (b) a second flange; (c) a ball; (d) an inner magneticcartridge; (e) an outer magnetic cartridge; (f) a planetary gearassembly; and (g) a pressure equalization system comprising an innerpressure equalization tube and an outer pressure equalization tube;wherein the inner magnetic cartridge is situated inside of the outermagnetic cartridge, and wherein the inner and outer magnetic cartridgesactuate the valve; wherein the planetary gear assembly is situatedbetween the inner magnetic cartridge and the ball; and wherein the innerequalization tube is situated inside of the outer equalization tube, anda piston and spring washer stack are situated between the inner andouter equalization tubes.
 7. The stemless ball valve of claim 6, whereinthe inner and outer equalization tubes each has a threaded end, andwherein the spring washer stack biases the piston toward the threadedend of the inner and outer equalization tubes.
 8. The stemless ballvalve of claim 6, wherein the inner and outer equalization tubes aresituated between the ball and the first flange.
 9. The stemless ballvalve of claim 6, wherein the inner and outer equalization tubes aresituated between the ball and the second flange.
 10. The stemless ballvalve of claim. 6, wherein the piston comprises at least one recess, andwherein an O-ring is situated in the recess to provide a seal betweenthe piston and the outer equalization tube.